Contra-rotating propulsor for marine propulsion

ABSTRACT

A system for providing marine propulsion is provided including an input shaft driven by a prime mover, a pinion gear coupled to the input shaft, a plurality of planet gears coupled to the pinion gear, a planet carrier having the plurality of planet gears rotationally mounted thereto, and a ring gear surrounding the planet gears and coupled thereto. The planet carrier and ring gear are coupled to internal and external output shafts that are coaxially aligned, which are coupled to aft and forward propulsor elements. The ring gear and planet carrier rotate in opposite directions to provide contra-rotating forward and aft propulsor elements. The ring gear and planet gear are each coupled to rotation altering devices that, when at least one is activated, the rotation of both the planet carrier and ring gear will be altered, thereby altering the rotation of the propulsor elements.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional PatentApplication No. 61/789,176, filed Mar. 15, 2013, which is herebyincorporated by reference in its entirety.

BACKGROUND

Marine or ship propulsion has been achieved in a variety of ways overtime, including the use of propulsor elements such as propellers orwaterjet impellers. Some of the primary challenges in designing a shippropulsion system include the matching of the propulsor elements(propellers or waterjet impellers) to the characteristics of the hullform, mission requirements, and the characteristics and limitations ofthe prime movers (e.g. diesel engines, gas turbines, electric motors).This is further complicated by the need to “balance” the performance ofthe system over the operating range of the prime mover.

Historically, ship propulsion systems have been optimized to address akey performance point for the application. For example, Ship Assist Tugsare normally optimized to maximize stationary pulling power, referred toas Bollard Pull, but in reality spend relatively little of their dutycycle at this operating point.

Sports fishing boats and Military Patrol Boats on the other hand arenormally optimized for top-end speed. Accordingly, the most efficientand affordable installations have prime movers, reduction gears, andfixed pitch propellers or waterjets that are selected to maximize thisdesired performance characteristic, and most often sacrificing betterperformance at “off-design” operating point where they spend most oftheir time.

Examples of prior art that attempt to address this conundrum include theimplementation of Controllable/Reversible Pitch Propellers and theimplementation of electric drive systems.

The former is a common attempt at solving this problem but thetrade-offs are: higher system acquisition cost; propeller blade shapethat is optimized for top speed or Bollard Pull characteristics but isless efficient when operating outside this range; and larger propellerpropulsor hub size with corresponding reduced overall efficiency.

The use of electric drives has the trade-off of being significantlyhigher in acquisition cost and has a lower operating efficiency over theentire operating range as a result of the mechanical-to-electrical powerconversion.

An additional and more substantial challenge has been identified inNaval Ship applications. Worldwide, these Naval Ships have evolved intofaster, smaller, more agile vessels, capable of operating at higherspeeds in shallower coastal environments. Examples include the US Navy'sLittoral Combat Ship and Joint High Speed Vessel. These are smaller,high horsepower ships capable of achieving speeds in excess of 35-40knots. Prior art in the form of conventional single-impeller waterjetshas been significantly challenged to “get the horsepower into the water”without causing destructive cavitation and without exceeding the spaceavailable on the transom of a narrow, high speed hullform.

Prior attempts to address this challenge using planetary gears with freerotation of planet carriers and ring gears to produce a contra-rotatingpropulsor fall short in their ability to maximize the efficiency of thesystem. Prior solutions impose a restraining element on only one or theother of the two output elements (planet carrier or ring gear, but notboth) and offer no provision for “redistributing” this restrainingenergy back into the system.

BRIEF SUMMARY

The proposed invention improves upon this prior art by offering a systemthat uses the efficiency of fixed pitch contra-rotating propulsors butprovides the ability to “adjust” or “balance” the system to improveefficiency over the entire operating range of the prime mover.

The proposed invention, when configured as a waterjet withcontra-rotating impellers, addresses the challenge of “gettinghorsepower in the water” by allowing the two impellers to be designed toincrease flow through the waterjet without incurring the negativeeffects of cavitation and at the same time allowing equivalent orgreater thrust to be developed using smaller diameter impellers (whichconsumes less transom real estate).

The proposed invention not only provides for this energy recovery, butby doing so, also provides a system that is immediately adaptable to amore flexible “Hybrid” configuration thereby further improving overallsystem efficiency and reduced fuel consumption.

The invention includes a device or system consisting of planetary gears;shafting; clutches; hydraulic or electric pumps, motors, and/orgenerators; and propelling devices (propellers or waterjets) that can beused in a contra-rotating arrangement to propel a boat or ship throughthe water.

A first embodiment of the invention includes a contra-rotating propulsorsystem having an input shaft coupled to a pinion gear, a planetary gearset, a planet carrier, and a ring gear, where the planet carrier iscoupled to a first output shaft and the ring gear is coupled to a secondcoaxial output shaft. The output shafts can each be coupled to propulsorelements such as propellers or waterjet impellers.

Another embodiment of the invention includes the propulsor system andfurther includes a first rotation altering element coupled to the planetcarrier and a second rotation altering element coupled to the ring gearto re-distribute the energy generated by the output shafts.

Another embodiment of the invention includes the propulsor system andfurther includes a reversing clutch coupled to the input shaft ormultiple clutches coupled to output shafts to reverse the rotation ofthe propulsor elements.

Another embodiment of the invention includes a single, variable speedelectric propulsion motor, either DC or AC, that is configured to allowboth an armature and outer opposed field windings mounted to a carrierto rotate freely and “counter-poised” against each other. The armatureis connected to a center, internal output shaft, and the outer fieldwindings carrier is connected a coaxial outer output shaft.

Another embodiment of the above described invention includes outer fixedfield windings that can be energized to either resist or brake therotation of either the armature or the field winding carrier, therebytransferring power from one to the other, and also allowing for directelectrical input or output to/from the system, thereby providing ahybrid capability.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1.1 is a schematic view of a first embodiment of a propulsor systemhaving propellers as the propulsor elements;

FIG. 1.2 is a schematic view of a second embodiment of the propulsorsystem having waterjet impellers as the propulsor elements;

FIG. 2.1 is a schematic view of a third embodiment of the propulsorsystem having a reversing clutch coupled to the input shaft;

FIG. 2.2 is a schematic view of a fourth embodiment of the propulsorsystem including reversing and ahead clutches coupled to the outputshafts;

FIG. 3.1 is a schematic view of a fifth embodiment of the propulsorsystem having braking mechanisms coupled to a planet gear and a ringgear of the propulsor system;

FIG. 3.2 is a schematic view of a sixth embodiment of the propulsorsystem having motor/generator feedback elements coupled to the planetgear and the ring gear and further coupled to a controller;

FIG. 3.3 is a schematic view of a seventh embodiment of the propulsorsystem having ring-type field windings disposed adjacent the ring gearand the planet gear and being coupled to a controller;

FIG. 3.4 is a schematic view of an eighth embodiment of the propulsorsystem having ring-type field windings disposed adjacent the ring gearand the planet gear and being coupled to a controller that is coupled toa power source of a ship;

FIG. 3.5 is a schematic view of a ninth embodiment of the propulsorsystem having ring-type field windings disposed adjacent the ring gearand the planet gear and being coupled to a hybrid controller that iscoupled to a power source of a ship and a battery bank;

FIG. 3.6 is a schematic view of a tenth embodiment of the propulsorsystem having hydraulic pump and motor feedback elements coupled to theplanet gear and ring gear;

FIG. 4.1 is a schematic view of an eleventh embodiment of the propulsorsystem incorporating a single main propulsion motor capable of freerotation of both a center armature and outer field windings withcontra-rotating outputs taken off the a center armature shaft and anouter field winding carrier respectively;

FIG. 4.2 is a schematic view of a twelfth embodiment of the propulsorsystem and similar to the system shown in FIG. 4.1, but also havingring-type field windings disposed adjacent to an armature and adjacentto a field winding carrier and being coupled to a controller; and

FIG. 4.3 is a schematic view of a thirteenth embodiment of the propulsorsystem having ring-type field windings disposed adjacent to an armatureand adjacent to a field winding carrier and being coupled to a hybridcontroller that is coupled to a power source of a ship and a batterybank

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

With reference to FIGS. 1.1 to 4.3, a contra-rotating propulsor system10 is provided having various embodiments described herein. Withreference to FIG. 1.1, the system 10 includes a main power source orprime mover 11 that is configured and arranged to drive an input shaft12 in a first rotary direction R1. The prime mover 11 and input shaft 12drives the system through the use of a pinion gear 13, a plurality ofplanet gears 14, a planet carrier 15, and a ring gear 16. Morespecifically, the pinion gear 13 is coupled to an end of the input shaft12 and is directly driven by the input shaft 12 such that the piniongear rotates in the same rotary direction R1 as the input shaft 12.

The planet gears 14 are arranged circumferentially around and mesh withthe pinion gear 13 and are each coupled to the planet carrier 15. Theplanet gears 14 can each rotate about their individual axes relative tothe planet carrier 15. The planet carrier 15 holds the planet gears 14in their orbital or radial position around the pinion gear 13, allowingthe carrier 15 (and the planet gears 14 coupled thereto) to rotatearound the pinion gear 13 and in the same rotational direction as thepinion gear 13 but at a different RPM depending on the relative diameterof the pinion gear 13 and planet gears 14. These gears 13 and 14 can bespur gears, single helical gears, or double helical gears. For the sakeof simplicity, only single helical gears are shown in FIG. 1.1. Whilethe planet carrier 15 rotates in the same rotational direction as thepinion gear 13, individual ones of the planet gears 14 rotate in theopposite rotational direction R2 due to meshing between the planet gears14 and the pinion gear 13, which have external teeth or other externalgearing arrangements that cause opposite rotation.

The planetary gear arrangement also contains the ring gear 16 thatsurrounds and meshes with the planet gears 14. This ring gear 16 isconfigured with internal teeth whereas the pinion gear and planet gearsare configured with external teeth. As shown in FIG. 1.1, the rotationaloutput from the ring gear 16 is opposite that of the pinion gear 13 andplanet carrier 15. The output RPM of the ring gear 16 will be dependenton the diameters of the pinion gear 13, planet gears 14, and ring gear16, as well as the relative RPMs of the pinion gear 13, planet carrier15, and ring gear 16, which is further described below.

In some prior planetary gear arrangements, either the planet carrier orthe ring gear is fixed in position, with the rotational output beingtaken off the un-fixed planet carrier or ring gear. In this invention,both the planet carrier 15 and the ring gear 16 are allowed to rotatefreely (or as described in further detail below, with either partial orfull constraint.

The ring gear 16 is coupled to an external output shaft 17, and theplanet carrier 15 is coupled to an internal output shaft 18. The outputshafts 17 and 18 are axially concentric, and the opposite rotation ofthe ring gear 16 and planet carrier 15 creates dual and contra-rotatingoutput paths through the output shafts 17 and 18. Each of these outputshafts 17 and 18 is therefore “counter-poised” against the other throughthe planetary gearing. The power output of each shaft 17 and 18 willtherefore be determined by the diameters of the pinion gear 13, planetgear 14, and ring gear 16, in conjunction with the torques applied bycontra-rotating forward propulsor element 19 and aft propulsor element20, further described below.

With reference to FIGS. 1.1 and 1.2, the forward propulsor elements 19and 23 are respectively coupled to the external output shaft 17, and theaft propulsor elements 20 and 24 are respectively coupled to theinternal output shaft 18. As shown in FIG. 1.1, the propulsor elements19 and 20 can be in the form of forward and aft propellers 21 and 22,respectively. As shown in FIG. 1.2, the propulsor elements 19 and 20 canbe in the form of forward and aft waterjet impellers 23 and 24,respectively. Because the propulsor elements 19 and 20 are coupled tothe external and internal output shafts 17 and 18, respectively, thepropulsor element 19 and 20 are contra-rotating.

In the case of waterjet impellers 23 and 24, these devices typicallyhave a unidirectional flow of water through the waterjet and incorporatea self-contained reversing and steering capability through the use ofsteering nozzles and reversing buckets.

The contra-rotating nature of the propulsor elements 19 and 20 createsan increased efficiency in marine propulsion. The system 10 describedabove can also have reduced size and weight relative to conventionalreduction gear and propeller systems known in the art, because the useof multiple planetary gears 14 with multiple torque transmission paths(one for each planet gear 14) allows each of the individual planet gears14 to be smaller and shorter in axial length relative to traditionalreduction gear and propeller systems. The size and weight of theplanetary gears 14 can also be reduced as a result of thecontra-rotation of the planet carrier 15 and ring gear 16 thateffectively produce a greater reduction gear ratio using smaller gearsto reduce size and weight of the system.

The system 10 can also provide equivalent thrust to a traditionalpropeller system while using propulsor elements 19 and 20 that have asmaller diameter relative to a traditional system, because total thrustoutput will be provided by the two contra-rotating propulsor elements 19and 20.

Moreover, the system 10 results in reduced cavitation relative to atraditional system. Cavitation can be reduced by selecting the diameter,RPM, number of blades, and blade shape of each of the twocontra-rotating propulsor elements 19, 20 specifically for the flowpattern, flow velocity, and flow direction that each of the two elements19, 20 is exposed to throughout the operating range. This capabilityalso allows for further increased efficiency and reduced cavitation,vibration, and noise.

Furthermore, by employing contra-rotating propulsor elements 19, 20configured in an axial arrangement, and by proper design of the aft(downstream) propulsor 20 (diameter, number of blades, bladepitch/angle, blade shape, etc.), the system 10 allows for the recoveryof rotational energy imparted to the water by the forward (upstream)propulsor 19.

In another form, and with reference to FIG. 2.1, the system 10 caninclude reversing capability. In this form, the system can includeintegral clutches 25 and 26. Clutch 25 is disposed on input shaft 12,while clutch 26 is disposed on an idler gear 27 that meshes with gearsof clutch 25. The clutches 25 and 26 are synchronized and controlled insuch a way as to allow the rotation of the pinion gear 13 to be reversedby reversing the rotation of the portion of the input shaft 12 that iscoupled to the pinion gear 13.

With reference to FIG. 2.2, the reversing capability of the system canbe provided in another form where the output shafts 17 and 18 can eachbe coupled to either the planet carrier 15 or ring gear 16. In thisform, the internal output shaft 18 is capable of being connected toeither the planet carrier 15 or ring gear 16 via clutches 27 and 28.More specifically, clutch 27 is an ahead clutch, and selectively couplesthe internal output shaft 18 to the planet carrier 15. Clutch 28 is areversing clutch, and selectively couples the internal output shaft 18to the ring gear 16. Similarly, the external output shaft 17 is capableof being connected to either the planet carrier 15 or the ring gear 16via clutches 29 and 30. More specifically, clutch 29 is an ahead clutch,and selectively couples the external shaft 17 to the ring gear 16.Clutch 30 is a reversing clutch and selectively couples the externalshaft 17 to the planet carrier 15. Clutches 27 and 29 can be engaged atthe same time to drive the output shafts 17 and 18 is the directionsdescribed above. To reverse the direction of the output shafts 17 and18, clutches 28 and 30 can be engaged.

The above reversing concepts are equally applicable to the propellerembodiment of FIG. 1.1 or the waterjet impeller embodiment of FIG. 1.2and provide significant advantages. In addition to advantages describedabove in relation to the system of FIGS. 1.1 and 1.2, there is increasedflexibility and applicability by allowing direct reversing of thecontra-rotating propulsor elements 19 and 20. The clutches 25 and 26coupled to the input shaft 12, and shown in FIG. 2.1, can allow fordisengagement of the prime mover 11 from the remainder of the system 10.Similarly, the clutches 27, 28, 29, 30 allow for disengagement of thepropulsor element 19 and 20 from the remainder of the system 10.Furthermore, by using the clutches 27, 28, 29, 30, the reversingcapability of the system 10 can be implemented without the use of idlergears, thereby increasing the efficiency of the system.

Turning now to FIGS. 3.1 to 3.6, the system 10 can be provided withdifferential capabilities. The planetary gearing arrangement describedabove can similarly apply. One configuration of a differentialcontra-rotating propulsor system 10 is depicted in FIG. 3.1. This systemcontains the same basic elements as described in reference to FIGS. 1.1and 1.2 above, but further includes a set of fully engaging or slippingclutch type brakes 31 and 32 attached to the planet carrier 15 and thering gear 16, respectively.

In operation, either one or the other of the clutch brakes 31 and 32 iseither partially or fully engaged, thereby restraining or stopping therotation of the engaged element (either the planet carrier 15 or thering gear 16). The result is that a portion or all of the input power isre-directed to the unrestrained output element. This “differential”capability allows for the re-distribution of power from one output shaftto the other so as to optimize the efficiency of the system throughoutthe operating range.

With reference to FIG. 3.2, a more flexible and versatile configurationof this same “differential” capability includes the replacement of theclutch brakes 31 and 32 described above with one or more sets ofelectrical “feedback” elements 33 and 34 that are engaged with theplanet carrier 15 and the ring gear 16, respectively.

As shown in FIG. 3.2, each of the elements 33 and 34 would be anelectric motor/generator configured and connected such that while oneset was energized as a generator, the other set would function as amotor. The electrical feedback elements 33 or 34 operating in generatormode act as restraining devices and the electrical power output fromthese generators can be “fed back” to the other of the electricalelements 33 or 34, which would function as motors.

This configuration would allow for more effective and efficient transferof power from the restrained output shaft to the unrestrained outputshaft. These electrical feedback elements 33 and 34 would be capable ofbeing energized so that power transfer from one of the output shafts 17or 18 to the other of the output shafts 17 or 18 could occur in eitherdirection and over a power range within the capabilities of theinstalled electrical feedback elements 33 and 34. The degree of“restraint” imposed by the generators 33 or 34 and the correspondingamount of “fed back” power through the motors 33 or 34 and oppositeturning output shafts 17 and 18 would be established by an electricalcontroller 35 that could be programed to adjust the distribution ofpower so as to maximize operating efficiency of the entire system.

The electrical feedback elements 33 and 34 could be configured as one ormore sets of elements on the same planetary gear depending on space,weight, and cost constraints as well as desired differential powercapabilities. For instance, the feedback elements 33 and 34 could eachbe a single element coupled to the carrier 15 and ring gear 16,respectively, or the elements 33 and 34 could each be a pair of elementscoupled to the carrier 15 and ring gear 16, respectively, or three ormore elements could be used. The number of elements for each of thefeedback elements 33 and 34 can be determined, in part, based on space,weight, and cost considerations.

With reference to FIG. 3.3, an alternative to the motor/generatorelectrical feedback elements 33 and 34 depicted in FIG. 3.2 can be inthe form of ring-type motor/generator field windings 36 and 37 on theperimeter of both the planet carrier 15 and ring gear 16, respectively.These ring-type field windings 36 and 37 can be energized similar to themotor/generators 33 and 34 depicted in FIG. 3.2 to achieve the same“resistive” and “feedback” effects, but without the mechanical lossesthat can be associated with the additional gear meshes that existbetween the electrical feedback elements 33 and 34 and the planetcarrier 15 and ring gear 16, respectively, shown in FIG. 3.2.

With reference to FIG. 3.4, a further enhancement or capability of theelectrical feedback elements described above includes an outside powersource 38 that the motor/generator elements 36 and 37 are connected to.The power source 38 can be in the form of generator power or batteries.The motor/generator elements 36 and 37 can be connected to the powersource 38 through the control device 35, such that the contra-rotatingoutput shafts 17 and 18 could be powered independently via electricalpower alone from the power source 38. This could be particularly usefulwhen operating at low power/loitering speeds and would allow operationwithout the prime mover 11 in operation.

The above depiction in FIG. 3.4 illustrates the motor/generator elementsin the form of the field windings 36 and 37, but could also apply to theelectrical feedback elements 33 and 34 described with reference to FIG.3.2. It will be appreciated that further reference to themotor/generator elements 36 and 37 can similarly apply to the electricalfeedback elements 33 and 34.

With reference to FIG. 3.5, the feedback elements 36 and 37 describedabove could also be connected to a hybrid external electrical controldevice 39 that would allow the entire system to be used in a “hybrid”fashion such that electrical power from the element(s) 36 and 37 actingas generators could be used to either charge storage batteries 40,connected to the hybrid controller 39, or supply supplementary power tothe ship's power source 38, or conversely, either the ship's onboardelectrical power from the power source 38 or ship's storage batteries 40could be used to supply additional “boost” power to the propulsionsystem 10.

With reference to FIG. 3.6, in another form, the electrical feedbackelements 36 and 37 described above could be replaced by hydraulicfeedback elements 41 and 42 in the form of hydraulic pump/motorelements. In this case, the hydraulic feedback elements 41 and 42 woulduse hydraulic fluid as a means of transferring power from one outputelement to the other.

Each of the above described “differential” embodiments can be combinedwith the reversing embodiments of FIGS. 2.1 and 2.2 described above toprovide the same advantages described in reference thereto.

Turning now to FIGS. 4.1 to 4.3, the system 10 can be configured as apurely electrical device by replacing the freely rotating planetary geararrangement with a freely rotating electric motor 40. In theseembodiments the system 10 becomes somewhat simpler but possesses some orall of the same characteristics described above.

The most basic form of this embodiment is depicted in FIG. 4.1 where avariable speed electric motor 50, which is either AC or DC is configuredwith slip-ring electrical inputs 52 so as to allow for the free rotationof an armature 54 and the outer field windings 56 which are attached toa rotating field winding carrier 58. In this embodiment, the internaloutput shaft 18 is connected to the armature 54 and rotates in the firstrotational direction R1. The external output shaft 17 is connected tothe outer field winding carrier 58 and rotates in the opposite directionR2. The armature 54 and the field winding carrier 58 are thereforecounter-poised against each other and are free to rotate, restrainedgenerally only by the torque imposed by the connected propulsor elements19 and 20, which are connected to the external output shaft 17 andinternal output shaft 18, respectively. The output horsepower of thesystem is increased or decreased by varying the input electrical powerto the motor 50 through an electrical controller 60.

FIG. 4.2 depicts a modified version of the system depicted in FIG. 4.1and incorporates a differential capability by imposing feedback elementsin the form of additional field windings 62 on both the armature 54 andthe motor field winding carrier 58. These field windings 62 can beeither energized as generators, thereby imposing a restraint on therotating element (the carrier 58 and or armature 54), or energized asmotors, thereby supplementing or adding to the rotational energy of therotating element. In this manner the differential capability workssimilar to the differential elements depicted in FIG. 3.4, with thedifferential distribution of power to each of the output shafts 19 and20 being controlled by the electrical controller 60.

FIG. 4.3 depicts a system similar to that depicted in FIG. 4.2 but withthe addition of Hybrid elements in the form of batteries 64 connected tothe controller 60.

Each of the above field windings 62, field windings 56, or slip-ringelectrical inputs 52 can also be referred to as rotational alteringelements.

The above embodiments relating to the “differential” conceptsillustrated in FIGS. 3.1 to 3.6 and 4.1 to 4.3 provide a variety ofadditional advantages. The above described brakes 31 and 32, electricalfeedback elements 33 and 34, field winding feedback elements 36 and 37,hydraulic feedback elements 41 and 42, field windings 56, and fieldwindings 62 that provide restraining capability allow for the controlleddistribution of power between the contra-rotating output shafts 17 and18 thereby giving the system 10 a “variable differential” capability.Moreover, these elements can be configured in size and quantity toprovide a range of power re-distribution or “differential” capability.These elements can be connected to allow power to be re-distributed ineither direction between the contra-rotating output shafts 17 and 18.

The above described hybrid capabilities can provide power generation toeither charge the shipboard batteries 40 or 64, or supply ship servicepower directly. This also provides the ability to use power from thebatteries 40 or 60, or the power source 38, to provide direct electricalpower to the contra-rotating shafts 17 and 18 without having to uselarger propulsion engines or motors such as the prime mover 11. Thebatteries 40 or 60, or power source 38, can provide additional boost oracceleration. Additionally, the electrical feedback elements can be usedas either a primary or backup starting motor for the prime mover 11. Theabove described “differential” capabilities provide a robust solution toallow for the efficiency of the system 10 to be optimized at alloperating points throughout the operating range of the system 10.

The above described embodiments of the system 10 can have numerousapplications. Examples include a similarly configured system on a shipassist tug. In this case, the differential contra-rotating propulsorsystem can be designed such that the freely rotating planet carrier 15and ring gear 16, without restraint applied thereto, could be optimizedfor maximum Bollard Pull (zero speed pulling power). When operating in aloitering condition at engine idle speeds, more of the engine outputpower could be re-directed to the aft (normally lower pitch) propulsor20 driven off of the planet carrier 15 thereby reducing the torque onthe prime mover 11 and improving efficiency in the process.Alternatively, the embodied Hybrid configuration of the invention couldoperate in electric mode, where ship's electrical power from the powersource 38 or batteries 40 or 60 could be used to provide loiteringcapability without the use of the prime mover 11.

In the case of a sport fishing boat or a military patrol boat, the “freerunning” (without restraint) system 10 could be optimized for top-endspeed. In the case of a sport fishing boat that operates for significantperiods at trolling speeds, the power from the prime mover 11 can be“redirected” to the lower pitch, aft propulsor 20 thereby reducingtorque on the engine and increasing efficiency. Similarly to the shipassist tug described above, this trolling mode could also beaccomplished through the use of the Hybrid capability, using solelyelectrical power from the power source 38, the batteries 40, or both forpropulsion.

Military patrol boats operate in a similar fashion with needs forrelatively short bursts at top-end speed and significant time spent atloiter speeds. A similar, more efficient distribution of propulsionpower could be used to meet these requirements.

The proposed invention configured as a waterjet with contra-rotatingimpellers 23 and 24 also addresses a modern challenge with newer, highspeed hullforms designed to operate in shallow, coastal environments.These hullforms favor the use of waterjets in order to maintain minimumdraft and achieve higher efficiency when operating at speeds greaterthan 30 knots. The use of a waterjet configuration of the proposedinvention will allow equal or greater thrust to be delivered through asmaller diameter waterjet without incurring the negative effects ofcavitation. This saves both space (transom area required for thewaterjet) and weight due to the use of a smaller, more axially orientedunit.

Other applications, such as LNG powered vessels, where there exists arequirement to “absorb” boil-off gas energy, even while loitering ortied to a pier, can be addressed using the proposed system. Electricalpower can be consumed through the use of the Hybrid capability where thepropulsor elements 19 and 20 can be driven by the ship's LNG powersource 38 to “oppose” each other, thereby expending energy withoutproducing thrust.

The system 10 is unconstrained in size and output power and cantherefore be applied to larger ships providing similar benefit.

While the above description constitutes the preferred embodiment of thepresent invention, it will be appreciated that the invention issusceptible to modification, variation and change without departing fromthe proper scope and fair meaning of the accompanying claims.

What is claimed is:
 1. A system for providing propulsion to a marinevessel, the system comprising: an input shaft defining a firstlongitudinal axis and configured for being rotatably driven by a primemover in a first rotary direction at a first angular velocity; arotatable pinion gear coupled to the input shaft, wherein the pinionrotates in the first rotary direction at the first angular velocity; aplurality of planet gears coupled to the pinion gear and havingindividual rotational axes for each of the plurality of planet gears,wherein each of the plurality of planet gears rotate about theirindividual rotational axis in a second rotary direction that is oppositethe first rotary direction of the pinion gear in response to rotation ofthe pinion gear in the first rotary direction; a planet carriersupporting each of the plurality of planet gears and holding theplurality of planet gears in the same orbital position around the piniongear, the planet carrier rotating in the first rotary direction inresponse to rotation of the pinion gear in the first rotary direction,wherein the planet carrier rotates at a second angular velocity that isdependent on the first angular velocity of the pinion gear and arelative diameter between the pinion gear and the plurality of planetgears; a ring gear surrounding the plurality of planet gears anddirectly engaged with each of the plurality of planet gears, the ringgear rotating in the second rotary direction corresponding to the secondrotary direction of each of the plurality of planet gears about theirindividual axes and opposite the first rotary direction in response torotation of the planet carrier and the pinion gear in the first rotarydirection, the ring gear rotating at a third angular velocity that isdependent on the first angular velocity of the pinion gear, the secondangular velocity of the planet carrier, and the relative diameterbetween the pinion gear and the plurality of planet gears; an internaloutput shaft coupled to the planet carrier and coaxial with the inputshaft and extending in first longitudinal direction away from the planetcarrier, the internal output shaft rotating in the first rotarydirection at the second angular velocity corresponding to the firstrotary direction and the second angular velocity of the planet carrier;an external output shaft coupled to the ring gear and coaxial with theinput shaft and the internal output shaft and extending in the firstlongitudinal direction away from the ring gear and surrounding theinternal output shaft, the external output shaft rotating in the secondrotary direction at the third angular velocity corresponding to thesecond rotary direction and the third angular velocity of the planetcarrier; a forward propulsor element coupled to the external outputshaft and rotatable therewith; an aft propulsor element coupled to theinternal output shaft and rotatable therewith; wherein the planetcarrier is freely rotatable and selectively constrainable between freerotation without constraint and a full constraint, wherein constraint isprovided by a first rotation altering element coupled to the planetcarrier and being selectively activatable for altering the rotationalspeed of the planet carrier; wherein the ring gear is freely rotatableand selectively constrainable between free rotation without constraintand full constraint, wherein constraint is provided by a second rotationaltering element coupled to the ring gear and being selectivelyactivatable for altering the rotational speed of the ring gear; whereinactivation of one of the first or second rotation altering elementsaffects the rotational speeds of both the ring gear and planet carrier;and wherein each of the plurality of planet gears are engaged with boththe pinion gear and the ring gear, with each of the plurality of planetgears being radially aligned and disposed radially between the piniongear and the ring gear, and wherein each of the plurality of planetgears are also supported by the planet carrier and will orbit around thepinion gear along with the rotation of the planet carrier.
 2. The systemof claim 1, wherein the propulsor elements comprise propellers.
 3. Thesystem of claim 1, wherein the propulsor elements comprise waterjetimpellers.
 4. The system of claim 1, wherein the input shaft includes areversing clutch mechanism coupled thereto.
 5. The system of claim 1,wherein the first and second rotation altering elements comprise firstand second clutch-type brakes to selectively decrease the speed of oneof the planet carrier or ring gear and increase the speed of the otherof the planet carrier or ring gear.
 6. The system of claim 1, whereinthe first and second rotation altering elements comprise first andsecond feedback elements.
 7. The system of claim 6, wherein the firstand second feedback elements comprise first and second electricalmotor/generators.
 8. The system of claim 6, wherein the first and secondfeedback elements comprise first and second ring-type field windings. 9.The system of claim 6, wherein the first and second feedback elementscomprise first and second hydraulic pump/motor elements.
 10. The systemof claim 6, wherein the first and second feedback elements are coupledto a controller for redistributing power from one of the feedbackelements to the other.
 11. The system of claim 10, wherein thecontroller is coupled to an auxiliary power source for driving thefeedback elements and the planet carrier or ring gear.
 12. The system ofclaim 10, wherein the controller comprises a hybrid controller.
 13. Asystem for providing propulsion to a marine vessel, the systemcomprising: an input shaft defining a first longitudinal axis andconfigured for being rotatably driven by a prime mover in a first rotarydirection; a rotatable pinion gear coupled to the input shaft androtatable in the first rotary direction in response to rotation of theinput shaft in the first rotary direction: a plurality of planet gearscoupled to the pinion gear and rotatable in an opposite rotary directionfrom the pinion gear; a planet carrier supporting each of the pluralityof planet gears, the planet carrier being rotatable in the same rotarydirection as the pinion gear; a ring gear surrounding the plurality ofplanet gears and being coupled thereto, the ring gear being rotatable inthe same rotary direction as individual ones of the plurality of planetgears and in the opposite rotary direction as the planet carrier andpinion gear; an internal output shaft coupled to the planet carrier; anexternal output shaft coupled to the ring gear and surrounding theinternal output shaft; a forward propulsor element coupled to theexternal output shaft; an aft propulsor element coupled to the internaloutput shaft; a first rotation altering element coupled to the planetcarrier and being selectively activatable for altering the rotationalspeed of the planet carrier; a second rotation altering element coupledto the ring gear and being selectively activatable for altering therotational speed of the ring gear; wherein activation of one of thefirst or second rotation altering elements affects the rotational speedsof both the ring gear and planet carrier; wherein the internal shaftincludes a first ahead clutch disposed between the aft propulsor elementand the planet carrier and a first reversing clutch disposed between theaft propulsor element and the ring gear, the external shaft includes asecond ahead clutch disposed between the forward propulsor and the ringgear and a second reversing clutch between the aft propulsor and theplanet carrier, the first and second ahead clutches are engaged at thesame time to drive the forward propulsor in a first direction and theaft propulsor in a second direction with the first and second reversingclutches disengaged, and the first and second reversing clutches areengaged at the same time to drive the forward propulsor in the seconddirection and the aft propulsor in the first direction while the firstand second ahead clutches are disengaged.